DE102019202447A1 - Transmission shaft, transmission and automotive powertrain - Google Patents

Abstract

Shaft (W) for a motor vehicle transmission (G), the shaft (W) having several axially aligned bores (B1, B2, B3, B4, B1RS, B_SE2, B_SE5) which are provided for guiding fluid within the shaft (W) are, the shaft (W) having a first, second and third axial section (W1, W2, W3), with a spatial arrangement of at least one of the bores (B2; B1), which at least in sections in the first section (W1) and is arranged radially spaced from an axis of rotation (WA) of the shaft (W), is arranged congruently with a spatial arrangement of at least one other of the bores (B1RS; B_SE5), which is arranged at least in sections in the third section (W3), as well as gears ( G) with such a shaft (W), as well as the drive train with such a gear (G).

Description

The invention relates to a shaft for a motor vehicle transmission, a transmission for a motor vehicle with such a shaft, and a drive train for a motor vehicle with such a transmission.

In the prior art it is known for motor vehicle transmissions to supply hydraulic fluid to elements of the transmission via bores running in a transmission shaft. So describes the DE 10 2013 219 631 A1 for example a system for supplying transmission elements with fluid. Several axially extending bores are arranged therein in an input shaft of the transmission. Fluid is supplied to the bores via five supply channels, which are arranged axially directly adjacent to one another. Oil can be fed to an actuation of a torque converter lock-up clutch via one of the feed channels and a bore arranged coaxially to the axis of rotation of the input shaft. One of the supply channels is connected to a further bore, which is also arranged coaxially to the axis of rotation.

With such a construction it is essential that the shaft still has sufficient strength despite the bores. An outer diameter of the shaft should be kept as small as possible in order to keep the diameter of the shaft bearings and of the sealing elements acting on the shaft small. It must also be noted that different pressures can act in the bores. If the wall thickness between the bores is too small, breakthroughs between the bores and thus hydraulic short circuits can occur during operation. The tolerances when producing the bores must be taken into account here, since a misalignment of the drilling axis can considerably reduce the wall thickness between the bores, particularly with relatively deep bores.

It is therefore the object of the invention to provide a shaft which is characterized by a high level of security against hydraulic short circuits.

The object is achieved by the features of claim 1. Advantageous embodiments result from the subclaims, the description and the figures.

A shaft for a motor vehicle transmission is proposed which has a plurality of axial bores. An axial bore is understood here to mean that the axis of such an axial bore is aligned axially parallel or coaxially to the axis of rotation of the shaft. The bores are distributed in the cross-sectional area of the shaft and are used to guide fluid within the shaft.

The shaft has first, second and third axial sections. The second section is disposed axially between the first and third sections. In other words, the second section is spatially located between the first and third sections. Fluid is supplied to the bores in the second section. In this second section, the shaft can have radial bores, for example, through which fluid can reach the various axial bores, starting from the outer diameter of the shaft. Fluid emerges from the bores in the first and third sections. For this purpose, the shaft can have radial bores in the first and third sections, through which fluid can pass from the axial bores to the outer diameter of the shaft. Alternatively or in addition, fluid can exit at the axial ends of the shafts.

According to the invention, a spatial arrangement of at least one of the axial bores, which is arranged radially spaced from the axis of rotation of the shaft, is congruent with a spatial arrangement of at least one other of the axial bores. One of these two congruently arranged axial bores is arranged in sections in the first section, but not in the third section. The other of these two congruently arranged bores is arranged at least in sections in the third section, but not in the first section.

A “congruent spatial arrangement” of two bores is understood to mean that the position of these bores in the cross section of the shaft is the same.

The two bores can have the same or different diameters. The axes of these two holes are coaxial with one another.

The design of the shaft according to the invention enables the risk of a hydraulic short circuit between the two axial bores to be reduced in a simple manner.

According to one possible embodiment, the number of axial bores running in the first section of the shaft differs from the number of bores running in the third section. For example, four axial bores can be arranged in the first section and three axial bores can be arranged in the third section. Because the solution according to the invention is particularly advantageous for shafts with a large number of axial bores, since the risk of a hydraulic short circuit is particularly high here.

Preferably, both the axial bores running in the first section and the third section are distributed uniformly in the cross section of the shaft. Such a uniform arrangement of the axial bores favors a high mechanical strength of the shaft.

According to a possible alternative embodiment, exactly two of the axial bores, which are spatially congruent, run in the first section and in the third section. According to a possible further alternative embodiment, exactly three of the axial bores, which are spatially congruent, run in the first section and in the third section. Since the solution according to the invention is particularly advantageous for shafts with a large number of axial bores, the proposed shaft is particularly suitable for these alternative configurations.

The shaft can preferably be part of a transmission for a motor vehicle. For example, the shaft can form a drive shaft of the transmission.

The transmission with the shaft can preferably have a hydrodynamic torque converter with a hydraulically actuatable lockup clutch and a plurality of hydraulically actuatable shifting elements. A gear formation of the transmission is controlled by selective actuation of the shift elements. Fluid is supplied to the torque converter and / or to actuate the lock-up clutch through one of the axial bores of the shaft, which is arranged in the first section of the shaft. If the torque converter is designed as a so-called two-line converter, the lock-up clutch is actuated via the fluid supply to the torque converter. If the torque converter is designed as a so-called three-line converter, a bore for supplying fluid to the torque converter and a separate bore for supplying fluid to actuate the lock-up clutch are preferably provided. A fluid supply for actuating at least one of the switching elements is preferably carried out through one of the axial bores, which is arranged in the third section of the shaft. Such a solution offers the advantage that the fluid can be supplied to the torque converter and / or the lock-up clutch actuation and to actuate at least one of the switching elements centrally on the second section of the shaft. Therefore, for example, a separate fluid supply channel on a front bearing plate of the transmission can be omitted.

The transmission preferably also has a hydraulically actuated separating clutch which is functionally arranged between an input hub of the transmission and the torque converter. A fluid supply for actuating the separating clutch is preferably carried out through one of the axial bores of the shaft, which is arranged in the first section. This solution also offers the advantage that a separate fluid supply channel for actuating the separating clutch on a front bearing plate of the transmission can be omitted.

According to a preferred embodiment, one of the axial bores, which is arranged in the first section of the shaft, serves to supply lubricating oil to elements of the transmission. Another of the axial bores, which is arranged in the third section of the shaft, also serves to supply lubricating oil to elements of the transmission. The transmission elements include, for example, toothing, roller bearings, slide bearings, thrust washers or vibration dampers.

The transmission according to one of the embodiments described above can be part of a drive train for a motor vehicle.

• 1a eine vereinfachte Darstellung eines Kraftfahrzeug- Antriebsstrangs mit einem Getriebe;
• 1b einen reduzierte Darstellung des Getriebes gemäß 1a;
• 2 und 3 je eine vereinfachte Schnittansicht eines Getriebes gemäß einem ersten möglichen Ausführungsbeispiel;
• 4 eine vereinfachte Schnittansicht eines Abschnitts eines Getriebes gemäß einem zweiten möglichen Ausführungsbeispiel;
• 5a bis 5c je einen Querschnitt einer Welle des Getriebes gemäß dem zweiten Ausführungsbeispiel.
• 6 eine vereinfachte Schnittansicht eines Abschnitts eines Getriebes gemäß einem dritten möglichen Ausführungsbeispiel;
• 7a und 7b je einen Querschnitt einer Welle des Getriebes gemäß dem dritten Ausführungsbeispiel;
• 8 eine vereinfachte Schnittansicht eines Abschnitts eines Getriebes gemäß einem vierten möglichen Ausführungsbeispiel;
• 9a und 9b je einen Querschnitt einer Welle des Getriebes gemäß dem vierten Ausführungsbeispiel;

Exemplary embodiments of the invention are described in detail below with reference to the accompanying figures. Show it:

• 1a a simplified representation of a motor vehicle drive train with a transmission;
• 1b a reduced representation of the transmission according to 1a ;
• 2 and 3 each a simplified sectional view of a transmission according to a first possible embodiment;
• 4th a simplified sectional view of a portion of a transmission according to a second possible embodiment;
• 5a to 5c each a cross section of a shaft of the transmission according to the second embodiment.
• 6th a simplified sectional view of a portion of a transmission according to a third possible embodiment;
• 7a and 7b each a cross section of a shaft of the transmission according to the third embodiment;
• 8th a simplified sectional view of a portion of a transmission according to a fourth possible embodiment;
• 9a and 9b each a cross section of a shaft of the transmission according to the fourth embodiment;

1a shows schematically a drive train of a motor vehicle. The drive train has an internal combustion engine VM , a transmission G with a wave W. and a differential gear AG on. The internal combustion engine VM is with an input hub ON of the transmission G connected. In this connection an in 1a Torsional vibration damper not shown be arranged. An output shaft FROM of the transmission G is with the differential gear AG connected, for example via a cardan shaft. By means of the differential gear AG becomes the one on the output shaft FROM applied power to drive wheels DW of the motor vehicle distributed. The in 1a The drive train shown is only to be regarded as an example. Instead of the structure shown with the drive train aligned longitudinally to the direction of travel of the motor vehicle, the transmission is also used G conceivable in a drive train oriented transversely to the direction of travel. The differential gear AG can in a housing GG of the transmission G be integrated.

The gear G has a hydrodynamic torque converter TC with an impeller P , a turbine wheel T , a guide wheel L. and a lock-up clutch WK on. By closing the lock-up clutch WK becomes the impeller P with the turbine wheel T connected. The idler L. is about a freewheel F. on one on the housing GG attached housing plate ZP supported. The turbine wheel T is with the wave W. connected. The gear G also has an electrical machine EM with a non-rotating stator S. and a rotatable rotor R. on. The rotor R. is with the impeller P connected, and via a disconnect clutch K0 with the input shaft ON connectable.

The gear G has a hydraulic unit HY on. The hydraulic unit HY has a pump, not shown, and a hydraulic switching device, not shown. The pump can supply hydraulic fluid to the hydraulic switching device. The hydraulic switching device is set up to transfer the hydraulic fluid to various hydraulic consumers of the transmission G to be divided as required. The case plate ZP has a first oil channel ZP1 , a second oil channel ZP2 , a third oil passage ZP3 and a fourth oil passage ZP4 on. The oil channels ZP1 to ZP4 serve to guide the oil from the hydraulic switchgear to the shaft W. . In the 1a shown arrangement of the oil channels ZP1 to ZP4 axially one behind the other is only to be viewed as an example and is mainly used for better illustration. To the transmission G Execute axially compact, all or some of the oil channels ZP1 to ZP4 be arranged in the same cross-sectional plane.

By means of the gearbox G can have different gear steps between the shaft W. and the output shaft FROM to be provided. This is what the gearbox G several planetary gear sets, which together as a gear set RS are designated. The wave W. serves as the drive shaft of the wheelset RS . The gear G also has several switching elements SE1 , SE2 , SE3 , SE4 , SE5 on. The switching elements SE1 , SE2 , SE3 , SE4 , SE5 work with the planetary gear sets to form the gearbox G together. The gear G as shown in 1a is only to be regarded as an example. Instead of the planetary gear sets, for example, spur gear sets can be used to form gears.

1b shows a reduced representation of the in 1a illustrated transmission G . There are only the wave W. with the associated turbine wheel T as well as the housing plate ZP shown. In 1b it becomes clear that the wave W. has three axial sections, namely a first section W1 , a second section W2 and a third section W3 . The second section W2 is axially between the first section W1 and the third section W3 arranged. In the second section W2 the fluid is supplied to in the shaft W. arranged in 1b Axial bores, not shown, via those in the housing plate ZP arranged oil channels ZP1 , ZP2 , ZP3 , ZP4 . Fluid emerges from the bores in the sections W1 and W3 . The section W3 is the wheelset RS assigned. The section W1 is the torque converter TC , the disconnect clutch K0 and the lock-up clutch WK assigned.

2 Figure 11 shows a simplified sectional view of a portion of the transmission G according to a first embodiment. The lock-up clutch WK is designed as a wet clutch and is operated by means of a piston WKK operated, which with a pressure chamber WKP is connected. The piston WKK is between two seals WKD1 , WKD2 guided. The printing room WKP is in sections through a radial wall X limited which with the impeller P connected is. A gap between the wall X and the wave W. is through a seal DX sealed.

The disconnect clutch K0 is about a piston COOK operated, which with a pressure chamber LAD is connected. The piston COOK is between two seals K0D1 , K0D2 guided. The printing room LAD is in sections through the wall X limited. To compensate for the pressure in the pressure room LAD acting rotational forces is a pressure equalization space KOA intended. The piston COOK is between the pressure space LAD and the pressure equalization space KOA arranged. The wave W. is on the input hub ON about a roller bearing WL stored so that the shaft W. around the axis of rotation WA is rotatably mounted. More, in 2 Rolling bearings, not shown, for supporting the shaft W. and the input hub ON be provided.

In 2 is the oil supply to the toroidal space of the torque converter TC , the oil supply to the rolling bearing WL as well as the lubricating oil supply to part of the wheelset RS shown. The cutting plane of the shaft W. is chosen so that an axial bore B1 and an axial bore B2 are visible. The axial bore B2 serves to supply oil to the toroidal space of the torque converter TC . Through a hole B2_in in the wave W. oil becomes a bore B2 supplied, the oil through a bore B2_out out of the wave W. can escape. The supply of oil into the bore B2_in takes place via the oil channel ZP2 . The hydraulic interface between the oil channel ZP2 and the bore B2_in is sealed with two sealing rings. The oil supply to the bores B1 and B2 takes place in the section W2 the wave W. . From the holes B1 and B2 the supplied oil enters the section W1 the wave W. out.

Through the hole B2_out becomes the lock-up clutch WK as well as the hydrodynamic path between the pump wheel P , Turbine wheel T and idler L. Oil supplied. The oil discharge from the toroidal space of the torque converter TC can be done, for example, through a gap between one with the pump wheel P connected housing of the torque converter TC and one with the idler L. connected shaft WLR is arranged. The corresponding oil path is in 2 indicated by arrows. Downstream of the bore B2_out is the hole B2 by a lock B2S locked.

The axial bore B1 serves to supply oil to the rolling bearing WL , to fill the pressure compensation chamber KOA and for supplying oil to the separating clutch K0 . Via the oil channel ZP1 oil becomes an annular gap B1R fed. Through a hole B1_in in the wave W. gets oil from the annular gap B1R for drilling B1 fed. Some of this oil occurs at an opening B1_out in the face of the shaft W. out. By the rotation of the shaft W. this oil becomes radially outward to an inner side of the input hub ON hurled. From there the oil flows through the roller bearing WL through towards the seal K0D2 . Through an axial gap between one axial end of the input hub ON and the piston COOK the oil enters the pressure equalization chamber K0A . If this is sufficiently filled with oil, the oil becomes the separating clutch K0 fed.

Coincident with the axial bore B2 is an axial hole B1RS arranged. The axial bore B1RS opens into the bore B1_in so that the oil, which is from the annular gap B1R into the hole B1_in is guided into the hole B1 and into the hole B1RS divides. About the hole B1RS oil becomes elements of the wheelset RS supplied, for example for lubrication. The oil supply to the drilling B1 RS takes place in the section W2 the wave W. ; the oil leak from the bore B1RS takes place in the section W3 the wave W. (not shown).

3 shows a further simplified sectional view of a portion of the transmission G according to the in 2 illustrated first embodiment. The cutting plane through the shaft W. was chosen so that an axial bore B3 and an axial bore B4 are visible. The axial bore B3 serves to supply oil to the pressure chamber WKP the lock-up clutch WK . The axial bore B4 serves to supply oil to the pressure chamber K0P of the separating clutch K0 .

The oil supply to the bore B3 takes place via the oil channel ZP3 in the housing plate ZP . Via the oil channel ZP3 oil gets into a bore B3_in in the wave W. which with the hole B3 connected is. That through the hole B3_in supplied oil passes through a bore B3_out in the printing room WKP one, between the seal DX and the seal WKD2 . Downstream of the bore B3_out is the hole B3 by a lock B3S locked. The hydraulic interface between the oil channel ZP3 and the bore B3_in is sealed with two sealing rings.

The oil supply to the bore B4 takes place via the oil channel ZP4 in the housing plate ZP . Via the oil channel ZP4 oil gets into a bore B4_in in the wave W. which with the hole B4 connected is. That through the hole B4_in supplied oil passes through a bore B4_out into the pressure chamber K0P, between the seal DX and the seal K0D2 . Downstream of the bore B4_out is the hole B4 by a lock B4S locked. The hydraulic interface between the oil channel ZP4 and the bore B4_in is sealed with two sealing rings.

The oil supply to the bores B3 and B4 takes place in the section W2 the wave W. . The oil leak from the holes B3 and B4 takes place in the section W1 the wave W. .

4th Figure 11 shows a simplified sectional view of a portion of the transmission G according to a second embodiment. The case plate ZP and the wave W. are constructed differently than in the first embodiment according to 2 and 3 . The housing plate has next to the oil channels ZP1 , ZP2 , ZP3 , ZP4 two additional oil channels ZP_SE2 and ZP_SE5 on to oil to a total of seven axial holes B1 , B2 , B3 , B4 , B1RS , B_SE2 , B_SE5 the wave W. feed.

Via the oil channel ZP4 oil gets into the axial bore B4 . That in the hole B4 The oil supplied is used to actuate the separating clutch K0 . Via an in 4th not shown in section W1 of the wave W. arranged radial bore, the oil comes out of the bore B4 into the pressure chamber K0P.

The hole B2 is in the sectional view of the shaft W. according to 4th not visible; it's just the radial feed hole B2_in indicated. That in the hole B2 supplied oil is used to supply oil to the torque converter TC . Via an in 4th not shown in section W1 the wave W. arranged radial bore, the oil comes out of the bore B2 to the lock-up clutch WK as well as the hydrodynamic path between the pump wheel P , Turbine wheel T and idler L. .

That in the hole B3 The oil supplied is used to operate the lock-up clutch WK . Via an in 4th not shown in section W1 the wave W. arranged radial bore, the oil comes out of the bore B3 in the printing room WKP .

That about a hole B_SE_in into the hole B_SE2 The oil supplied is used to actuate the switching element SE2 , which acts as a coupling between two shafts of the wheel set RS is executed. Via an in 4th not shown in section W3 the wave W. arranged radial bore, the oil comes out of the bore B_SE2 into a pressure chamber for actuating the switching element SE2 .

That in the annular gap B1R The oil supplied is used to supply oil to the rolling bearing WL , to fill the pressure compensation chamber K0A , for supplying oil to the separating clutch K0 as well as for the oil supply to the lubrication points of the wheelset RS . The gap B1R is about the radial hole B1_in with the axial bore B1 connected. That in the hole B1 The oil supplied is used to supply oil to the rolling bearing WL , to fill the pressure compensation chamber KOA and for supplying oil to the separating clutch K0 . That in the hole B1 supplied oil occurs at one axial end of the shaft W. in the section W1 off (in 4th not shown). The gap B1R is also about a radial hole B1RS_in with the axial bore B1RS connected. That in the hole B1RS supplied oil emerges from one or more radial bores in the section W3 the wave W. are arranged (in 4th not shown). The radial holes B1RS_in and B1_in have a different diameter. This allows the oil to be distributed between the bores B1 and B1 RS be influenced in a simple way.

That about a hole B_SE5_in into the hole B_SE5 The oil supplied is used to actuate the switching element SE5 , which acts as a coupling between two shafts of the wheel set RS is executed. Via an in 4th not shown in section W3 the wave W. arranged radial bore, the oil comes out of the bore B_SE5 into a pressure chamber for actuating the switching element SE5 .

In the in 4th The second embodiment shown are the axial bores B1 and B_SE5 arranged congruently. This is illustrated below by the sectional views of the shaft W. in 5a to 5c described.

5a shows the cross section of the shaft W. in cutting plane AA , as in 4th specified. In the cutting plane AA are the holes B1RS , B_SE2 and B_SE5 visible. The angular position of the hole B_SE5 is highlighted. The holes B1RS , B_SE and B_SE5 lead starting from the section W2 to section W3 the wave W. . The holes B1RS , B_SE and B_SE5 are uniform in the cross section of the shaft W. distributed.

5b shows the cross section of the shaft W. in section plane BB, as in 4th specified. The holes are in section plane BB B1RS , B_SE2 and B1 visible. The angular position of the hole B1 is highlighted. Compared to 5a it becomes clear that the drilling B1 and B_SE5 are arranged congruently.

5c shows the cross section of the shaft W. in cutting plane CC , as in 4th specified. In the cutting plane CC are the holes B1 , B2 , B3 , B4 visible. The holes B1 , B2 , B3 , B4 lead starting from the section W2 to section W1 the wave W. . The holes B1 , B2 , B3 , B4 are uniform in the cross section of the shaft W. distributed.

6th Figure 11 shows a simplified sectional view of a portion of the transmission G according to a third embodiment. The case plate ZP and the wave W. are constructed differently than in the first two exemplary embodiments. The housing plate has four oil channels ZP1a , ZP2a , ZP3a , ZP4a to add oil to a total of four, in 6th not visible axial holes B1a , B2a , B3a , B4a the wave W. feed. The supply of oil from the oil ducts ZP1a , ZP2a , ZP3a , ZP4a into the respectively assigned hole B1a , B2a , B3a , B4a takes place through sealed annular gaps, in the same way as in 4th shown.

The oil channel ZP1a leads oil to the bore B1a to. The oil channel ZP2a leads oil to the bore B2a to. The oil channel ZP3a leads oil to the bore B3a to. The oil channel ZP4a leads oil to the bore B4a to. The supply of oil from the oil channels ZP1a , ZP2a , ZP3a , ZP4a into the respectively assigned hole B1a , B2a , B3a , B4a takes place in the section W2 the wave W. . The holes B1a and B2a run from the section W2 to section W1 but not to the section W3 . The holes B3a and B4a run from the section W2 to section W3 but not to the section W1 . The oil leak from the holes B1a and B2a takes place in the section W1 the wave W. . Of the Oil leakage from the holes B3a and B4a takes place in the section W3 the wave W. .

In the in 6th The third embodiment shown are the axial bores B1a and B3a arranged congruently. Furthermore, the axial bores B2a and B4a arranged congruently. This congruent arrangement is evident from the sectional views of the shaft W. in 7a and 7b clarified.

8th Figure 11 shows a simplified sectional view of a portion of the transmission G according to a fourth embodiment. The case plate ZP and the wave W. are constructed differently than in the first three exemplary embodiments. The housing plate has six oil channels ZP1a , ZP2a , ZP3a , ZP4a , ZP5a , ZP6a around oil to a total of six, in 8th not visible axial holes B1a , B2a , B3a , B4a , B5a , B6a the wave W. feed. The supply of oil from the oil ducts ZP1a , ZP2a , ZP3a , ZP4a , ZP5a , ZP6a into the respectively assigned hole B1a , B2a , B3a , B4a , B5a , B6a takes place through sealed annular gaps, in the same way as in 4th shown.

The oil channel ZP1a leads oil to the bore B1a to. The oil channel ZP2a leads oil to the bore B2a to. The oil channel ZP3a leads oil to the bore B3a to. The oil channel ZP4a leads oil to the bore B4a to. The oil channel ZP5a leads oil to the bore B5a to. The oil channel ZP6a leads oil to the bore B46 to. The supply of oil from the oil channels ZP1a , ZP2a , ZP3a , ZP4a , ZP5a , ZP6a into the respectively assigned hole B1a , B2a , B3a , B4a , B5a , B6a takes place in the section W2 the wave W. . The holes B1a , B2a , B5a run from the section W2 to section W1 but not to the section W3 . The holes B3a , B4a , B6a run from the section W2 to section W3 but not to the section W1 . The oil leak from the holes B1a , B2a and B5a takes place in the section W1 the wave W. . The oil leak from the holes B3a , B4a and B6a takes place in the section W3 the wave W. .

In the in 8th The fourth embodiment shown are the axial bores B1a and B3a arranged congruently. Furthermore, the axial bores B2a and B6a arranged congruently. Furthermore, the axial bores B5a and B4a arranged congruently. This congruent arrangement is evident from the sectional views of the shaft W. in 9a and 9b clarified.

List of reference symbols

VM

Internal combustion engine

G

transmission

ON

Input hub

FROM

Output shaft

GG

casing

ZP

Housing plate

ZP1

Oil channel

ZP2

Oil channel

ZP3

Oil channel

ZP4

Oil channel

ZP_SE2

Oil channel

ZP_SE5

Oil channel

ZP1a

Oil channel

ZP2a

Oil channel

ZP3a

Oil channel

ZP4a

Oil channel

ZP5a

Oil channel

ZP6a

Oil channel

W.

wave

WA

Axis of rotation

W1

First section of the wave

W2

Second section of the wave

W3

Third section of the wave

B1R

Annular gap

B1

Axial bore

B1RS

Axial bore

B2

Axial bore

B3

Axial bore

B4

Axial bore

B_SE2

Axial bore

B_SE5

Axial bore

B1a

Axial bore

B2a

Axial bore

B3a

Axial bore

B4a

Axial bore

B5a

Axial bore

B6a

Axial bore

B1_in

drilling

B1RS_in

drilling

B1_out

drilling

B2_in

drilling

B2_out

opening

B3_in

drilling

B3_out

drilling

B4_in

drilling

B4_out

drilling

B_SE2_in

drilling

B_SE5_in

drilling

B2S

Clasp

B3S

Clasp

B4S

Clasp

TC

Torque converter

P

Impeller

T

Turbine wheel

L.

Idler

WLR

Stator shaft

F.

Freewheel

WK

Lock-up clutch

WKP

Printing room

WKK

piston

WKD1

poetry

WKD2

poetry

X

Wall

DX

poetry

K0

Disconnect clutch

K0D1

poetry

K0D2

poetry

LAD

Printing room

COOK

piston

KOA

Pressure equalization space

EM

Electric machine

S.

rotor

R.

stator

WL

roller bearing

HY

Hydraulic unit

RS

Wheelset

SE1

Switching element

SE2

Switching element

SE3

Switching element

SE4

Switching element

SE5

Switching element

AG

Differential gear

DW

drive wheel

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• DE 102013219631 A1 [0002]

Claims (12)

Shaft (W) for a motor vehicle transmission (G), the shaft (W) having several axial bores (B1, B2, B3, B4, B1RS, B_SE2, B_SE5, B1a, B2a, B3a.) Distributed in the cross-sectional area of the shaft (W) , B4a, B5a, B6a), which are provided for guiding fluid within the shaft (W), - the shaft (W) having a first (W1), a second (W2) and a third axial section (W3) - the second section (W2) being arranged axially between the first (W1) and the third section (W3), - with a fluid supply to the bores (B1, B2, B3, B4, B1RS, B_SE2, B_SE5, B1a, B2a, B3a, B4a, B5a, B6a) takes place in the second section (W2), - whereby a fluid exit from the bores (B1, B2, B3, B4, B1RS, B_SE2, B_SE5, B1a, B2a, B3a, B4a, B5a, B6a) takes place in the first and third section (W1, W3), characterized in that a spatial arrangement of at least one of the bores (B2; B1, B1a), which is at least partially in the first section (W1) and radially spaced is arranged by an axis of rotation (WA) of the shaft (W), congruent with a spatial arrangement of at least one other of the bores (B1RS; B_SE5, B3a) is arranged, which is arranged at least in sections in the third section (W3). Wave (W) after Claim 1 , characterized in that the number of bores (B1, B2, B3, B4) running in the first section (W1) differs from the number of bores (B1RS, B_SE2, B_SE5) running in the third section (W3). Wave (W) after Claim 2 , characterized in that four of the bores (B1, B2, B3, B4) are arranged in the first section (W1), and that three of the bores (B1RS, B_SE2, B_SE5) are arranged in the third section (W3). Wave (W) after one of the Claims 1 to 3 , characterized in that the bores (B1, B2, B3, B4) running in the first section (W1) are evenly distributed in the cross section of the shaft (W), and that the bores (B1RS, B_SE2, B_SE5) are evenly distributed in the cross section of the shaft (W). Wave (W) after Claim 1 , characterized in that the shaft (W) has exactly four axial bores (B1a, B2a, B3a, B4a), two of the bores (B1a, B2a) at least partially in the first section (W1) and two of the bores (B3a, B4a) ) are arranged at least in sections in the third section (W3), the two bores (B1a, B2a) running in the first section (W1) being arranged congruently with the two bores (B3a, B4a) running in the third section (W3). Wave (W) after Claim 1 , characterized in that the shaft (W) has exactly six axial bores (B1a, B2a, B3a, B4a, B5a, B6a), three of the bores (B1a, B2a, B5a) at least in sections in the first section (W1) and three of the bores (B3a, B4a, B6a) are arranged at least in sections in the third section (W3), the three bores (B1a, B2a, B5a) running in the first section (W1) congruent with the three bores running in the third section (W3) (B3a, B4a, B6a) are arranged. Transmission (G) for a motor vehicle, characterized by a shaft (W) according to at least one of the preceding claims. Gear (G), characterized in that the shaft (W) forms a drive shaft of the gear (G). Gearbox (G) Claim 7 or Claim 8 , characterized in that the transmission (G) has a hydrodynamic torque converter (TC) with a hydraulically actuated lock-up clutch (WK), as well as several hydraulically actuable shifting elements (SE1, SE2, SE3, SE4, SE5), whereby by selective actuation of the shifting elements ( SE1, SE2, SE3, SE4, SE5) a gear formation of the transmission (G) can be controlled, - with a fluid supply to the torque converter (TC) and / or to actuate the lock-up clutch (WK) through one of the bores (B2, B3) of the shaft (W), which is arranged in the first section (W1) of the shaft (W), - and wherein a fluid supply for actuating at least one of the switching elements (SE2, SE5) through one of the bores (B_SE2, B_SE5) of the shaft (W ) takes place, which is arranged in the third section (W1) of the shaft (W). Gearbox (G) Claim 9 , characterized in that the transmission (G) furthermore has a hydraulically actuated separating clutch (K0) which is functionally arranged between an input hub (AN) of the transmission (G) and the torque converter (TC), a fluid supply for actuating the separating clutch ( K0) through one of the bores (B4) of the shaft (W), which is arranged in the first section (W1) of the shaft (W). Gearbox (G) Claim 9 or Claim 10 , characterized in that one of the bores (B1) arranged in the first section (W1) and one of the bores (B1_RS) arranged in the third section (W3) are provided for supplying lubricating oil to elements of the transmission (G). Drive train for a motor vehicle, characterized by a transmission (G) according to one of the Claims 7 to 11 .

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